US4086036A - Diaphragm pump - Google Patents

Diaphragm pump Download PDF

Info

Publication number
US4086036A
US4086036A US05/686,659 US68665976A US4086036A US 4086036 A US4086036 A US 4086036A US 68665976 A US68665976 A US 68665976A US 4086036 A US4086036 A US 4086036A
Authority
US
United States
Prior art keywords
diaphragm
housing
pumping chamber
fluid pump
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/686,659
Other languages
English (en)
Inventor
Loren M. Hagen
Ashwin H. Desai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Cole Parmer Instrument Co
Original Assignee
Cole Parmer Instrument Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Cole Parmer Instrument Co filed Critical Cole Parmer Instrument Co
Priority to US05/686,659 priority Critical patent/US4086036A/en
Priority to CA273,811A priority patent/CA1066557A/en
Priority to GB10631/77A priority patent/GB1530096A/en
Priority to DE19772713599 priority patent/DE2713599A1/de
Priority to FR7712493A priority patent/FR2352178A1/fr
Priority to JP5524777A priority patent/JPS52140005A/ja
Application granted granted Critical
Publication of US4086036A publication Critical patent/US4086036A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms

Definitions

  • This invention relates to fluid pumps and more particularly to flexible diaphragm pumps which will efficiently pump either liquids or gases.
  • a pumping chamber of variable volume is defined in part by a flexible diaphragm, usually circular, which is suitably clamped around its circumference.
  • Valves of simple design are provided in an inlet and an outlet leading to the pumping chamber, and pumping action is achieved by the reciprocation of the diaphragm so as to alternately increase and then decrease the volume of the pumping chamber.
  • On the suction stroke fluid is drawn in through the inlet valve while the outlet valve remains closed. Thereafter, on the discharge stroke, the intake valve closes, and the fluid is discharged through the outlet valve.
  • U.S. Pat. No. 3,461,808 shows a liquid pump of this type wherein a handle is provided for manual actuation of the diaphragm.
  • U.S. Pat. No. 3,273,505 shows a fuel pump of this type which utilizes an electromagnet to drive the diaphragm on one stroke and a spring to drive it on the return stroke.
  • U.S. Pat. No. 2,711,134 is similar except that it substitutes a source of high-pressure liquid for the electromagnet to achieve the power stroke.
  • U.S. Pat. No. 3,152,726 shows a pump of this general type which is driven from an electric motor via a linkage that includes a rotary cam which alternately lifts and then drops a roller attached to a plunger that reciprocates the diaphragm.
  • a major deficiency of diaphragm pumps of this type is the limited life of the flexible diaphragm because its failure renders the pump inoperative until replacement is effected.
  • pumps of this type have been used for pumping gases, e.g., to create a vacuum or superatmospheric air pressure, such pumps have not achieved truly satisfactory operation.
  • Another object of the invention is to provide a diaphragm pump adapted to be driven from the shaft of an electric motor which is simple in design but extremely effective in pumping characteristics.
  • a further object of the invention is to provide a diaphragm pump of simple design which is capable of high speed operation and which has an improved diaphragm lifetime without sacrificing pumping characteristics.
  • Still another object of the invention is to provide a diaphragm pump of simple construction which will create an effective vacuum when driven via a relatively inexpensive linkage from the output shaft of an electric motor.
  • FIG. 1 is a perspective view showing a fluid pump embodying various features of the invention mounted upon an electric motor and operatively connected to the shaft thereof;
  • FIG. 2 is an enlarged vertical sectional view taken generally along the line 2--2 of FIG. 1, showing the diaphragm at the bottom of the suction stroke;
  • FIG. 3 is a view similar to FIG. 2 showing only the pump mechanism and illustrating the diaphragm where it has reached a point near the end of the discharge stroke;
  • FIG. 4 is a view similar to FIG. 3 showing the diaphragm just beginning the suction stroke
  • FIG. 5 is an enlarged fragmentary view showing a portion of the pump as depicted in FIG. 3;
  • FIG. 6 is a sectional view taken through the center of the diaphragm subassembly showing the diaphragm, in full lines, in its unstressed condition and showing, in broken lines, the condition of the diaphragm at the very end of the discharge stroke and at the very end of the suction stroke.
  • FIG. 1 Shown in FIG. 1 is a pump 11 embodying various features of the invention mounted in operating position on an end of a standard electric motor 13. Although the motor itself forms no part of the present invention, the comparison afforded by FIG. 1 shows the relative smallness and compactness of the pump 11 compared to the usual size of a fractional horsepower AC electric motor.
  • a coupling 15 is suitably mounted to the rotary shaft 17 of the electric motor 13, which coupling carries an eccentrically mounted stub shaft 19.
  • the eccentric stub shaft 19 is received within the inner race of a ball bearing bushing 21 and traces a circular path or orbit (see FIG. 4, dot-dash line with reference letter "O") as the shaft 17 of the electric motor rotates about its axis.
  • the pump 11 includes a two-piece housing 22 made up of an upper head section 23 and a lower main body section 25.
  • a two-piece housing 22 made up of an upper head section 23 and a lower main body section 25.
  • the two sections 23,25 of the pump housing are preferably molded from a durable, corrosion-resistant plastic material, for example, Noryl, a polyphenylene oxide resin marketed by General Electric Company, although other suitable materials can be used.
  • the head 23 is tightly joined to the top of the body section 25 of the housing by four screws 27.
  • brass inserts (not shown) are preferably molded in four bosses 29 which are appropriately angularly spaced about the top of the body section 25.
  • a circular mounting flange 31 is provided as an integral part of the housing body section 25, which flange has four holes through which threaded bolts 33 from the electric motor protrude and upon which nuts 35 are installed to complete the mounting.
  • the body section 25 includes a hollow cylindrical casing 37 having a vertical axis which is integral with and extends forward from the mounting flange 31.
  • An enlarged hole 39 allows motor shaft 17, the coupling 15 and some of the attached linkage to be inserted therethrough into the cylindrical casing 37.
  • the lower end of the casing 37 is closed by an aluminum disc 41 or the like.
  • the head section 23 of the housing is molded to provide an inlet 43 and an outlet 45 for the pump.
  • the inlet 43 includes an uppermost threaded hole 47 for receiving a threaded coupling for attachment to a fluid inlet line.
  • a stepped passageway 49 Interconnecting this threaded hole 47 and the underside of the head 23 is a stepped passageway 49 having three different diameter sections.
  • the uppermost smallest diameter section remains empty and provides an undersurface against which a valve member, a small circular disc 51, abuts to close the inlet 43 during the discharge stroke of the pump.
  • the valve disc 51 is trapped in the intermediate passageway section by a rigid, apertured retainer 53 which is press-fit, or otherwise suitably secured, in the lowermost section of the passageway 49 which has the greatest diameter.
  • the holes in the retainer 53 are elongated and are positioned so that it is impossible for the valve disc 51 to close the holes when the valve is open, as shown in FIG. 2, whereas the diameter of the disc is sufficient to assure that it will totally close the smallest diameter section of the passageway 49 during the discharge stroke.
  • valve member should seat properly on the valve seat and provide a proper seal, and second, the valve member should not unnecessarily stick to the valve seat but should precisely follow the diaphragm movement.
  • valve body is made from one thermoplastic material, it has been found that improved results are obtained by forming the valve members from a different thermoplastic material. In the present case, very satisfactory results are obtained by molding the head 23 from polyphenylene oxide and stamping the valve disc 51 from polytetrafluoroethylene.
  • the outlet 45 is similarly formed with an uppermost threaded section 55 and a stepped lower passageway 57 of three different diameter sections, with the smallest diameter section being that which connects with the underside of the head section 23 of the housing.
  • a circular valve disc member 59 is again entrapped within the intermediate section by an apertured retainer 61 which is secured in the uppermost section, and the stepped passageway 57, the disc and the retainer together constitute the outlet valve.
  • the diaphragm assembly is shown by itself in FIG. 6 and comprises a flexible diaphragm 63 plus a reinforcing or center plate subassembly that includes a rigid post 65 which extends downward from the center of a rigid circular plate 67, formed of steel or the like.
  • the post 65 is drilled, and the drilled hole is provided with internal threads 69 which receive mating threads on a bolt 71.
  • the eccentric 19 on the motor shaft coupling 15 is press-fit within the inner race of the bushing 21, and a clamp 73 is fit about the outer race of the bushing.
  • the clamp 73 is formed with an upper bracket portion 75 that contains an aperture through which the bolt 71 is inserted prior to the installation of the clamp about the outer race of the bushing 21, and the tightening of a screw and nut 77 effects the final joinder.
  • the flexible diaphragm 63 is made from a durable, preferably chemical-resistant, synthetic rubber or elastomer material, and it is preferably molded about the center plate 67 subassembly, which would be provided as an insert in the mold cavity using conventional molding techniques.
  • the flexible diaphragm 63 can be made from Nitrile or Viton synthetic elastomer. As a result of the molding process, the rear surface of the center of the flexible diaphragm 63 is in adherent contact with the upper surface of the rigid plate 67 and thus effectively transmits the force from the rotating shaft 17 to the diaphragm.
  • the firm connection between the plate subassembly and the flexible diaphragm is enhanced by the total surrounding of the outer circumference of the plate 67 by the diaphragm 63 as a result of an inward-extending flange 79 which is created as a part of the molding process.
  • the diaphragm 63 is generally planar in configuration and is circular in outline.
  • An upstanding bead 81 is molded at the very circumference of the diaphragm 63, which assures the tight entrapment of the entire periphery of the diaphragm between the mating sections 23,25 of the pump housing.
  • the depth of a circular groove 83 cut in the undersurface of the head 23 is less than the height of the peripheral bead 81 but slightly greater in radial dimension, so that the bead is squeezed to cause it to fill the groove and bulge slightly outward into a pocket 85 provided in the upper surface of the housing body when the head is mated to the body 25.
  • This arrangement of placing the bead 81 in vertical compression effectively clamps the flexible diaphragm 63 within the housing 22 without stressing the diaphragm in a radial direction, which would create stresses contributing to wear deterioration.
  • the flexible diaphragm 63 is formed with an upstanding arcuate convolution or ridge 87 which provides an important function in assuring a long lifetime for the diaphragm.
  • the upper surface of the diaphragm 63, when clamped in position, together with the undersurface of the head section 23 of the housing defines the pumping chamber 89. With respect to the pumping chamber 89, the arcuate ridge 87 is convex.
  • the pump 11 is shown with the diaphragm 63 in its lowermost position where it resides at the completion of the suction stroke, at which instant the pumping chamber is at its largest volume.
  • the eccentric 19 is at the lowermost point of its orbit and is in vertical alignment below the rotating motor shaft 17, which is shown in FIG. 2 in dotted lines.
  • the diaphragm has flexed in the location of the arcuate ridge 87, and it can be seen that the arcuate ridge has substantially disappeared, having been blended into a relatively smooth curve.
  • the dimensioning of the arcuate ridge 87 is such that substantially no stretching has occurred in the diaphragm; instead, there has merely been a straightening-out of the arcuate ridge section.
  • the outlet or discharge valve is still in the closed position with the valve disc 59 seated against the upper exit from the smallest section of the passageway and that the inlet valve remains in the open position, as it has been throughout this half of the cycle allowing the entry of fluid through the apertured retainer 53 and into the pumping chamber 89.
  • the diaphragm which has been substantially displaced from its unstressed planar condition, extends downward from the clamped bead 81 at its perimeter and is supported by the curved surface 91 of inward extending flange 93 formed at the upper end of the cylindrical body casing 37 which is in the form of a section of the surface of an annulus.
  • the reinforcing plate 67 will rock downward and to the left, as viewed in FIG. 2, while the right-hand side begins to elevate.
  • This further lowering or dipping of the left-hand edge of the central portion of the diaphragm 63 results in a further simultaneous flexing and straightening of the diaphragm in this region as the left-hand edge is dipping to its lowest point.
  • the underside of the housing head 23 is formed with an annular surface portion 95 having a radius of curvature that is substantially matched to the radius of curvature of the upper surface of the diaphragm in a region 97 at the radially outer edge of the arcuate ridge 87.
  • the radius of this annular surface section 95 is within 5 percent of the radius of curvature of the corresponding region 97 of the upper surface of the diaphragm.
  • the curvature of the right-hand section of the upwardly distended diaphragm 63 fairly closely follows the curvature of the supporting undersurface portion 95 of the head.
  • the length of actual contact between the two surfaces will depend upon the pressure in the pumping chamber 89 and will usually be longer at the beginning of the suction cycle depicted in FIG. 4.
  • Minimizing the flexing which occurs in the diaphragm reduces stresses and heat build-up and increases its lifetime, and particularly important is the flexing of the arcuate ridge region when it is in its convex orientation as depicted in FIGS. 3 and 4.
  • the separation of the wear regions is best illustrated in FIG. 5 wherein the diameter of the annular surface section 95 formed on the underside of the head 23 is labeled D 1 , and the diameter of the annular surface portion 91 provided on the inwardly extending flange 93 of the body casing 37 is labeled D 2 .
  • the thickness of the diaphragm 63 is substantially constant throughout the region of the arcuate ridge 87, through the flat section radially outward thereof, and substantially all the way to the transition into the upstanding circumferential bead 81.
  • the difference in the diameters D 1 and D 2 should be equal to an amount at least four times the thickness of the diaphragm in this region and preferably at least six times the thickness. This difference is equal to twice the distance marked by the reference letter in FIG. 5. Stated in another way, the distance A which is the radial distance between the center points for the radii of curvature of the supporting surface portions of the upper and lower housing sections 23,25 should be equal to at least twice and preferably three times the thickness of this diaphragm region.
  • the region where the greatest amount of wear occurs along the lower surface of the diaphragm 63 is effectively separated from the region where the greatest amount of wear occurs along the upper surface of the diaphragm, and thus the contributions of the wear to the ultimate failure of the membrane are not additive, resulting in a substantially longer membrane lifetime.
  • the matching of the radius of curvature of the annular section 95 of the head to the corresponding curved region in the diaphragm translates the flexing of the diaphragm occurring at the left-hand region in FIG. 3 into a rolling action upward along the supporting surface, and likewise causes the diaphragm region to roll off the supporting arcuate surface during the early part of the suction stroke as depicted in FIG. 4, minimizing the bending stress which occurs at the upper surface of the membrane.
  • the pumping efficiency is affected by the amount of dead volume remaining in the pumping chamber 89 at the conclusion of the pumping or discharge stroke.
  • the illustrated pump 11 has been found to be extremely effective in pumping gases for the purpose of creating a vacuum or superatmospheric air pressure.
  • One of the contributing factors to its good efficiency is the high speed which is obtainable from the rotating shaft of an electric motor using the illustrated linkage, so long as the diaphragm design is such that it has a reasonably long lifetime.
  • Another contributing factor is the provision of a depending projection 99 in the undersurface of the head section 23 of the housing which is compatible with the rocking movement of the diaphragm and the effect of which is perhaps best seen in FIGS. 3 and 4.
  • the projection 99 runs diametrically across the undersurface of the head in a direction perpendicular to the centerline upon which the inlet 43 and outlet 45 are located.
  • the cross section of the projection 99 relative to what would otherwise be a flat central portion of the housing head is that of a trapezoid.
  • the projection 99 significantly reduces the dead volume of the pumping chamber (shown in FIG. 4), and its trapezoidal shape provides clearance for the upper surface of the central portion of the diaphragm in its canted orientation depicted in FIG. 3.
  • the diaphragm pump 11 provided by the invention is very simple in design and construction and small in size, it has proved to be efficient in pumping operation.
  • the high speed operation available from an electric motor e.g., 1550 r.p.m. for a 1/45 HP motor
  • renders it capable of transferring relatively large amounts of fluid e.g., 900 cu. in. of air per min.
  • the pumping chamber itself is relatively small in volume, capable of delivering air at about 20 psig and also capable of creating an excellent vacuum (e.g., 22 inches of Hg.).
  • the pump design renders it well suited for the transfer of liquids, and particularly corrosive chemicals, because the liquid being pumped need not contact any metal; of course, liquids would be pumped using a slower r.p.m.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Diaphragms And Bellows (AREA)
US05/686,659 1976-05-17 1976-05-17 Diaphragm pump Expired - Lifetime US4086036A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US05/686,659 US4086036A (en) 1976-05-17 1976-05-17 Diaphragm pump
CA273,811A CA1066557A (en) 1976-05-17 1977-03-11 Diaphragm pump
GB10631/77A GB1530096A (en) 1976-05-17 1977-03-14 Diaphragm pump
DE19772713599 DE2713599A1 (de) 1976-05-17 1977-03-28 Stroemungsmittelpumpe, insbesondere membranpumpe
FR7712493A FR2352178A1 (fr) 1976-05-17 1977-04-26 Pompe a membrane
JP5524777A JPS52140005A (en) 1976-05-17 1977-05-13 Liquid pumps

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US05/686,659 US4086036A (en) 1976-05-17 1976-05-17 Diaphragm pump

Publications (1)

Publication Number Publication Date
US4086036A true US4086036A (en) 1978-04-25

Family

ID=24757209

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/686,659 Expired - Lifetime US4086036A (en) 1976-05-17 1976-05-17 Diaphragm pump

Country Status (6)

Country Link
US (1) US4086036A (enrdf_load_stackoverflow)
JP (1) JPS52140005A (enrdf_load_stackoverflow)
CA (1) CA1066557A (enrdf_load_stackoverflow)
DE (1) DE2713599A1 (enrdf_load_stackoverflow)
FR (1) FR2352178A1 (enrdf_load_stackoverflow)
GB (1) GB1530096A (enrdf_load_stackoverflow)

Cited By (57)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4181477A (en) * 1978-03-02 1980-01-01 Pace Incorporated Pump valve
US4230025A (en) * 1978-11-02 1980-10-28 Jamesbury Corporation Pneumatic actuator
US4286932A (en) * 1978-02-14 1981-09-01 Nippondenso Co., Ltd. Diaphragm pump
USD262884S (en) 1980-01-29 1982-02-02 The Coca-Cola Company Fluid pump or similar article
US4334838A (en) * 1980-01-29 1982-06-15 The Coca-Cola Company Diaphragm type fluid pump having a flexible diaphragm with an internal reinforcing plate
US4406591A (en) * 1981-01-19 1983-09-27 Anthony Louis Electromagnetic fluid pump
US4492284A (en) * 1981-08-24 1985-01-08 Honda Giken Kogyo Kabushiki Kaisha Apparatus for arranging oil pressure pump in motor-cycle
US4571160A (en) * 1984-07-24 1986-02-18 The Mead Corporation Diaphragm pump having a flat plate actuating member slidable in slots
US4594059A (en) * 1981-11-28 1986-06-10 Erich Becker Diaphragm pump
US4597723A (en) * 1982-06-07 1986-07-01 Sember Joseph A Low pressure air supply and control system
US4762794A (en) * 1983-05-13 1988-08-09 Stephan Nees Apparatus for contacting biological cell systems with a perfusion fluid
US4773832A (en) * 1983-10-25 1988-09-27 Accuspray, Inc. Pump
US4774874A (en) * 1987-03-26 1988-10-04 Carmeli Adahan Rolling diaphragm construction and piston-cylinder assembly including same particularly useful for suction or compression pumps
US4776771A (en) * 1986-09-19 1988-10-11 Grunbeck Wasseraufbereitung Gmbh Metering pump
US4842498A (en) * 1987-01-20 1989-06-27 Thomas Industries, Inc. Diaphragm compressor
US4860640A (en) * 1986-12-03 1989-08-29 Neway Corp. Air operated diaphragm spring brake
US4864918A (en) * 1986-11-07 1989-09-12 The Gates Rubber Company Thermoplastic diaphragm
US4936758A (en) * 1987-08-10 1990-06-26 Aci Medical, Inc. Diaphragm pump
US4940399A (en) * 1987-12-01 1990-07-10 Pacesetter Infusion, Ltd. Piston cap and boot seal for a medication infusion system
US4951554A (en) * 1989-01-19 1990-08-28 American Standard Inc. Low stress diaphragm
US5325667A (en) * 1988-12-08 1994-07-05 Humanteknik Ab Machine for transforming pressure or potential energy of a fluid into mechanical work
WO1994017307A1 (en) * 1993-01-29 1994-08-04 Abbott Laboratories Method of testing for leakage in a solution pumping system
US5437218A (en) * 1994-04-04 1995-08-01 Pcm Pompes Diaphragm pump having variable displacement
US5507217A (en) * 1994-09-30 1996-04-16 Indian Head Industries, Inc. Perforate diaphragm alignment system for spring brake actuators
US5554014A (en) * 1993-08-25 1996-09-10 Knf Neuberger Gmbh Diaphragm pump with at least two diaphragms
FR2780476A1 (fr) * 1998-06-30 1999-12-31 Peugeot Dispositif de transmission d'un volume de fluide sous pression et membrane pour un tel dispositif
US6162028A (en) * 1996-08-02 2000-12-19 Robert Bosch Gmbh Fuel pumping device for two-stroke engines with an additional driving unit
US6338295B1 (en) * 1999-03-30 2002-01-15 Mikuni Adec Corporation Fuel pump
US6607361B1 (en) * 1998-09-25 2003-08-19 Bombardier Motor Corporation Of America Pumping method and device
US20040071572A1 (en) * 2001-01-02 2004-04-15 Andy Greter Diaphragm pump
US6796215B1 (en) * 1999-08-26 2004-09-28 Knf Neuberger Gmbh Membrane pump
US20040262563A1 (en) * 2003-05-13 2004-12-30 Gemu Gebruder Muller Apparatebau Gmbh & Co. Kg Compressor for a diaphragm valve
US20060213661A1 (en) * 2005-03-28 2006-09-28 Jackson Thomas R Fluid recovery system and method
US20080038125A1 (en) * 2006-08-09 2008-02-14 Alps Electric Co., Ltd. Piezoelectric pump and piezoelectric vibrator
US20090246035A1 (en) * 2008-03-28 2009-10-01 Smiths Medical Asd, Inc. Pump Module Fluidically Isolated Displacement Device
US20100021326A1 (en) * 2008-07-24 2010-01-28 Fujifilm Corporation Method fo pumping agglomerative liquid and method of producing recording medium
US20100135829A1 (en) * 2008-11-28 2010-06-03 Rinnai Corporation Air supply fan device
US20100158708A1 (en) * 2008-12-19 2010-06-24 Fuksa Richard C Two-stage membrane pump with economical inlet port design
US20100175550A1 (en) * 2009-01-15 2010-07-15 Rhoads David C Air Brake Diaphragms
KR100989585B1 (ko) 2008-08-29 2010-10-25 최영준 가진 유닛 및 이를 이용한 그라우팅 장치
US20110040252A1 (en) * 2007-10-16 2011-02-17 Peter Gravesen Cannula Insertion Device and Related Methods
US20110043357A1 (en) * 2009-08-18 2011-02-24 Greg Peatfield Methods for detecting failure states in a medicine delivery device
US20120107150A1 (en) * 2010-11-02 2012-05-03 Bogdan Pawlak Radial Diaphragm Pump
US20120312399A1 (en) * 2010-02-18 2012-12-13 Grundfos Management A/S Dosing pump
US20130042753A1 (en) * 2010-02-27 2013-02-21 Knf Neuberger Gmbh Diaphragm pump
US20130202416A1 (en) * 2010-10-08 2013-08-08 Ulvac, Inc. Drive device
US20130323099A1 (en) * 2012-05-31 2013-12-05 Industrial Technology Research Institute Synthetic jet equipment
US8672873B2 (en) 2009-08-18 2014-03-18 Cequr Sa Medicine delivery device having detachable pressure sensing unit
US20140134023A1 (en) * 2012-11-15 2014-05-15 Mindray Medical Sweden Ab Progressive pump force regulation
US9211378B2 (en) 2010-10-22 2015-12-15 Cequr Sa Methods and systems for dosing a medicament
US20160069340A1 (en) * 2013-03-06 2016-03-10 Suzhou Ecovas Commercial Robotics Co., Ltd. Dual-chamber dual-action air pump and glass-wiping robot having the air pump
US10173183B2 (en) 2014-09-11 2019-01-08 Flowserve Management Company Diaphragm pump with improved tank recirculation
US10578092B2 (en) * 2016-03-18 2020-03-03 Deka Products Limited Partnership Pressure control gaskets for operating pump cassette membranes
CN112628455A (zh) * 2013-06-24 2021-04-09 丹佛斯公司 用于动力阀的膜
US11117560B2 (en) * 2016-08-02 2021-09-14 Wabco Europe Bvba Membrane valve arrangement
US20220106955A1 (en) * 2020-10-07 2022-04-07 Alfmeier Präzision SE Diaphragm Assembly
US20240041578A1 (en) * 2014-12-01 2024-02-08 Water Pik, Inc. Oral irrigator

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2418352A1 (fr) * 1978-02-27 1979-09-21 Joint Francais Membrane de pompe
DE3018687C2 (de) * 1980-05-16 1986-10-30 J. Wagner Gmbh, 7990 Friedrichshafen Membran für Hochdruckförderpumpen, Kompressoren oder dgl.
DE3402472A1 (de) * 1984-01-25 1985-08-01 Joseph A. Oxnard Calif. Sember III Niederdruck-luftversorgungs- und steuersystem
DE8525733U1 (de) * 1985-09-10 1987-01-15 Becker, Erich, 7812 Bad Krozingen Membranpumpe
US4722230A (en) * 1986-05-29 1988-02-02 Graco Inc. Pressure gauge for high pressure flow through diaphragm pump
DE19635458A1 (de) * 1996-08-31 1998-03-05 Tiefbohrtechnik Gmbh Tbt Membranpumpe
JP4059973B2 (ja) * 1998-03-30 2008-03-12 パロマ工業株式会社 ガス湯沸器の水栓
EP1725792B1 (en) * 2004-03-16 2013-01-30 Hargraves Technology Corporation Pump sealing apparatus
JP5366649B2 (ja) * 2009-05-15 2013-12-11 トーステ株式会社 樹脂ダイヤフラム式流体制御弁
JP5302176B2 (ja) 2009-12-16 2013-10-02 多田プラスチック工業株式会社 流体用ダイヤフラムポンプ
DE102015016265A1 (de) * 2015-12-15 2017-06-22 Wabco Europe Bvba Ventileinheit zur Druckmodulation in einer Druckluft-Bremsanlage
US10422331B2 (en) 2016-08-12 2019-09-24 Ingersoll-Rand Company One piece diaphragm
DE102024202002A1 (de) * 2024-03-04 2025-09-04 Spx Flow Technology Germany Gmbh Membranpumpe

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR937214A (fr) * 1946-08-16 1948-08-11 Dispositif pour maintenir automatiquement le plein d'air dans un système à liquidesous pression
US2711134A (en) * 1950-07-26 1955-06-21 Infilco Inc Chemical feeder
US2742785A (en) * 1954-04-29 1956-04-24 Weatherhead Co Meter diaphragm
US3021792A (en) * 1959-10-30 1962-02-20 Acf Ind Inc Fuel pump diaphragm mounting
US3415198A (en) * 1966-08-16 1968-12-10 George J. Lappo Pump
US3461808A (en) * 1967-07-03 1969-08-19 Wood John Co Diaphragm hand pumps
GB1197226A (en) * 1966-10-20 1970-07-01 Erich Becker Improvements in or relating to Diaphragm Pumps
US3900276A (en) * 1973-05-16 1975-08-19 Mcculloch Corp Diaphragm pump method and apparatus
US3936245A (en) * 1972-04-03 1976-02-03 Johnson Service Company Fluid compressing apparatus
US3947156A (en) * 1972-03-08 1976-03-30 Erich Becker Diaphragm pump, particularly for the generation of vacuum
US3999899A (en) * 1974-05-29 1976-12-28 Toyota Jidosha Kogyo Kabushiki Kaisha Diaphragm fluid pump

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE502350A (enrdf_load_stackoverflow) *
DE826244C (de) * 1949-07-29 1951-12-27 Chausson Usines Sa Kolbenpumpe oder Verdichter

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR937214A (fr) * 1946-08-16 1948-08-11 Dispositif pour maintenir automatiquement le plein d'air dans un système à liquidesous pression
US2711134A (en) * 1950-07-26 1955-06-21 Infilco Inc Chemical feeder
US2742785A (en) * 1954-04-29 1956-04-24 Weatherhead Co Meter diaphragm
US3021792A (en) * 1959-10-30 1962-02-20 Acf Ind Inc Fuel pump diaphragm mounting
US3415198A (en) * 1966-08-16 1968-12-10 George J. Lappo Pump
GB1197226A (en) * 1966-10-20 1970-07-01 Erich Becker Improvements in or relating to Diaphragm Pumps
US3461808A (en) * 1967-07-03 1969-08-19 Wood John Co Diaphragm hand pumps
US3947156A (en) * 1972-03-08 1976-03-30 Erich Becker Diaphragm pump, particularly for the generation of vacuum
US3936245A (en) * 1972-04-03 1976-02-03 Johnson Service Company Fluid compressing apparatus
US3900276A (en) * 1973-05-16 1975-08-19 Mcculloch Corp Diaphragm pump method and apparatus
US3999899A (en) * 1974-05-29 1976-12-28 Toyota Jidosha Kogyo Kabushiki Kaisha Diaphragm fluid pump

Cited By (81)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4286932A (en) * 1978-02-14 1981-09-01 Nippondenso Co., Ltd. Diaphragm pump
US4181477A (en) * 1978-03-02 1980-01-01 Pace Incorporated Pump valve
US4230025A (en) * 1978-11-02 1980-10-28 Jamesbury Corporation Pneumatic actuator
USD262884S (en) 1980-01-29 1982-02-02 The Coca-Cola Company Fluid pump or similar article
US4334838A (en) * 1980-01-29 1982-06-15 The Coca-Cola Company Diaphragm type fluid pump having a flexible diaphragm with an internal reinforcing plate
US4406591A (en) * 1981-01-19 1983-09-27 Anthony Louis Electromagnetic fluid pump
US4492284A (en) * 1981-08-24 1985-01-08 Honda Giken Kogyo Kabushiki Kaisha Apparatus for arranging oil pressure pump in motor-cycle
US4594059A (en) * 1981-11-28 1986-06-10 Erich Becker Diaphragm pump
US4597723A (en) * 1982-06-07 1986-07-01 Sember Joseph A Low pressure air supply and control system
US4762794A (en) * 1983-05-13 1988-08-09 Stephan Nees Apparatus for contacting biological cell systems with a perfusion fluid
US4773832A (en) * 1983-10-25 1988-09-27 Accuspray, Inc. Pump
US4571160A (en) * 1984-07-24 1986-02-18 The Mead Corporation Diaphragm pump having a flat plate actuating member slidable in slots
US4776771A (en) * 1986-09-19 1988-10-11 Grunbeck Wasseraufbereitung Gmbh Metering pump
US4864918A (en) * 1986-11-07 1989-09-12 The Gates Rubber Company Thermoplastic diaphragm
US4860640A (en) * 1986-12-03 1989-08-29 Neway Corp. Air operated diaphragm spring brake
US4842498A (en) * 1987-01-20 1989-06-27 Thomas Industries, Inc. Diaphragm compressor
US4774874A (en) * 1987-03-26 1988-10-04 Carmeli Adahan Rolling diaphragm construction and piston-cylinder assembly including same particularly useful for suction or compression pumps
US4936758A (en) * 1987-08-10 1990-06-26 Aci Medical, Inc. Diaphragm pump
US4940399A (en) * 1987-12-01 1990-07-10 Pacesetter Infusion, Ltd. Piston cap and boot seal for a medication infusion system
US5325667A (en) * 1988-12-08 1994-07-05 Humanteknik Ab Machine for transforming pressure or potential energy of a fluid into mechanical work
US4951554A (en) * 1989-01-19 1990-08-28 American Standard Inc. Low stress diaphragm
WO1994017307A1 (en) * 1993-01-29 1994-08-04 Abbott Laboratories Method of testing for leakage in a solution pumping system
US5336053A (en) * 1993-01-29 1994-08-09 Abbott Laboratories Method of testing for leakage in a solution pumping system
US5554014A (en) * 1993-08-25 1996-09-10 Knf Neuberger Gmbh Diaphragm pump with at least two diaphragms
US5437218A (en) * 1994-04-04 1995-08-01 Pcm Pompes Diaphragm pump having variable displacement
US5507217A (en) * 1994-09-30 1996-04-16 Indian Head Industries, Inc. Perforate diaphragm alignment system for spring brake actuators
US6162028A (en) * 1996-08-02 2000-12-19 Robert Bosch Gmbh Fuel pumping device for two-stroke engines with an additional driving unit
FR2780476A1 (fr) * 1998-06-30 1999-12-31 Peugeot Dispositif de transmission d'un volume de fluide sous pression et membrane pour un tel dispositif
WO2000000743A1 (fr) * 1998-06-30 2000-01-06 Automobiles Peugeot Pompe a membrane et membrane pour une telle pompe
US6607361B1 (en) * 1998-09-25 2003-08-19 Bombardier Motor Corporation Of America Pumping method and device
US6338295B1 (en) * 1999-03-30 2002-01-15 Mikuni Adec Corporation Fuel pump
US6796215B1 (en) * 1999-08-26 2004-09-28 Knf Neuberger Gmbh Membrane pump
US7070400B2 (en) * 2001-01-02 2006-07-04 Medela Ag Diaphragm pump with eliminated pump chamber dead space, and circular recesses on the reverse side of the diaphragm for improved diaphragm chamber wall adherence
US20040071572A1 (en) * 2001-01-02 2004-04-15 Andy Greter Diaphragm pump
US7614606B2 (en) * 2003-05-13 2009-11-10 Gemü Gebrüder Müller Apparatebau GmbH & Co. KG Compressor for a diaphragm valve
US20040262563A1 (en) * 2003-05-13 2004-12-30 Gemu Gebruder Muller Apparatebau Gmbh & Co. Kg Compressor for a diaphragm valve
US20060213661A1 (en) * 2005-03-28 2006-09-28 Jackson Thomas R Fluid recovery system and method
US7255175B2 (en) 2005-03-28 2007-08-14 J&J Technical Services, L.L.C. Fluid recovery system and method
US20080038125A1 (en) * 2006-08-09 2008-02-14 Alps Electric Co., Ltd. Piezoelectric pump and piezoelectric vibrator
US20110040252A1 (en) * 2007-10-16 2011-02-17 Peter Gravesen Cannula Insertion Device and Related Methods
US9968747B2 (en) 2007-10-16 2018-05-15 Cequr Sa Cannula insertion device and related methods
US9005169B2 (en) 2007-10-16 2015-04-14 Cequr Sa Cannula insertion device and related methods
US20090246035A1 (en) * 2008-03-28 2009-10-01 Smiths Medical Asd, Inc. Pump Module Fluidically Isolated Displacement Device
US20100021326A1 (en) * 2008-07-24 2010-01-28 Fujifilm Corporation Method fo pumping agglomerative liquid and method of producing recording medium
US8297939B2 (en) * 2008-07-24 2012-10-30 Fujifilm Corporation Method of pumping agglomerative liquid and method of producing recording medium
KR100989585B1 (ko) 2008-08-29 2010-10-25 최영준 가진 유닛 및 이를 이용한 그라우팅 장치
US20100135829A1 (en) * 2008-11-28 2010-06-03 Rinnai Corporation Air supply fan device
US20100158708A1 (en) * 2008-12-19 2010-06-24 Fuksa Richard C Two-stage membrane pump with economical inlet port design
US8287249B2 (en) 2008-12-19 2012-10-16 Gardner Denver Thomas, Inc. Two-stage membrane pump with economical inlet port design
US20100175550A1 (en) * 2009-01-15 2010-07-15 Rhoads David C Air Brake Diaphragms
US8256341B2 (en) 2009-01-15 2012-09-04 Haldex Brake Corporation Air brake diaphragms
US10226588B2 (en) 2009-08-18 2019-03-12 Cequr Sa Methods for detecting failure states in a medicine delivery device
US9039654B2 (en) 2009-08-18 2015-05-26 Cequr Sa Medicine delivery device having detachable pressure sensing unit
US8547239B2 (en) 2009-08-18 2013-10-01 Cequr Sa Methods for detecting failure states in a medicine delivery device
US9694147B2 (en) 2009-08-18 2017-07-04 Cequr Sa Methods for detecting failure states in a medicine delivery device
US8672873B2 (en) 2009-08-18 2014-03-18 Cequr Sa Medicine delivery device having detachable pressure sensing unit
US9174009B2 (en) 2009-08-18 2015-11-03 Cequr Sa Methods for detecting failure states in a medicine delivery device
US10300196B2 (en) 2009-08-18 2019-05-28 Cequr Sa Medicine delivery device having detachable pressure sensing unit
US20110043357A1 (en) * 2009-08-18 2011-02-24 Greg Peatfield Methods for detecting failure states in a medicine delivery device
US9022972B2 (en) 2009-08-18 2015-05-05 Cequr Sa Medicine delivery device having detachable pressure sensing unit
US20120312399A1 (en) * 2010-02-18 2012-12-13 Grundfos Management A/S Dosing pump
US9057366B2 (en) * 2010-02-27 2015-06-16 Knf Neuberger Gmbh Diaphragm pump
US20130042753A1 (en) * 2010-02-27 2013-02-21 Knf Neuberger Gmbh Diaphragm pump
US20130202416A1 (en) * 2010-10-08 2013-08-08 Ulvac, Inc. Drive device
US9211378B2 (en) 2010-10-22 2015-12-15 Cequr Sa Methods and systems for dosing a medicament
US20120107150A1 (en) * 2010-11-02 2012-05-03 Bogdan Pawlak Radial Diaphragm Pump
US8974193B2 (en) * 2012-05-31 2015-03-10 Industrial Technology Research Institute Synthetic jet equipment
US20130323099A1 (en) * 2012-05-31 2013-12-05 Industrial Technology Research Institute Synthetic jet equipment
US9360004B2 (en) * 2012-11-15 2016-06-07 Shenzhen Mindray Bio-Medical Electronics Co., Ltd. Progressive pump force regulation
US20140134023A1 (en) * 2012-11-15 2014-05-15 Mindray Medical Sweden Ab Progressive pump force regulation
US20160069340A1 (en) * 2013-03-06 2016-03-10 Suzhou Ecovas Commercial Robotics Co., Ltd. Dual-chamber dual-action air pump and glass-wiping robot having the air pump
CN112628455A (zh) * 2013-06-24 2021-04-09 丹佛斯公司 用于动力阀的膜
CN112628455B (zh) * 2013-06-24 2023-02-21 丹佛斯公司 用于动力阀的膜
US10173183B2 (en) 2014-09-11 2019-01-08 Flowserve Management Company Diaphragm pump with improved tank recirculation
US20240041578A1 (en) * 2014-12-01 2024-02-08 Water Pik, Inc. Oral irrigator
US12383387B2 (en) * 2014-12-01 2025-08-12 Water Pik, Inc. Oral irrigator
US10578092B2 (en) * 2016-03-18 2020-03-03 Deka Products Limited Partnership Pressure control gaskets for operating pump cassette membranes
US10941760B2 (en) * 2016-03-18 2021-03-09 Deka Products Limited Partnership Pressure control gaskets for operating pump cassette membranes
US11117560B2 (en) * 2016-08-02 2021-09-14 Wabco Europe Bvba Membrane valve arrangement
US20220106955A1 (en) * 2020-10-07 2022-04-07 Alfmeier Präzision SE Diaphragm Assembly
US12012950B2 (en) * 2020-10-07 2024-06-18 Alfmeier Präzision SE Diaphragm assembly

Also Published As

Publication number Publication date
GB1530096A (en) 1978-10-25
CA1066557A (en) 1979-11-20
FR2352178A1 (fr) 1977-12-16
JPS52140005A (en) 1977-11-22
JPH0127271B2 (enrdf_load_stackoverflow) 1989-05-29
FR2352178B1 (enrdf_load_stackoverflow) 1983-10-21
DE2713599A1 (de) 1977-12-08
DE2713599C2 (enrdf_load_stackoverflow) 1988-12-15

Similar Documents

Publication Publication Date Title
US4086036A (en) Diaphragm pump
US8083506B2 (en) Double action simplex pump
US3947156A (en) Diaphragm pump, particularly for the generation of vacuum
US6506033B2 (en) Miniature pump with ball-plate drive
US5791882A (en) High efficiency diaphragm pump
US4305702A (en) Pump with expandable chamber
EP0210315B1 (en) Diaphragm pump, particularly with three working chambers
US4242061A (en) Double diaphragm pump
JP5600326B2 (ja) １つまたは複数のらせん状に延びるフィーチャを有する蛇腹プランジャ、そのような蛇腹プランジャを含むポンプ、および関連する方法
CN1071849C (zh) 一种往复泵
US7214042B2 (en) Progressing cavity pump with dual material stator
JP3976677B2 (ja) 支持リングを有する膜ポンプ
US3703342A (en) Fuel pump bellows construction
US4433966A (en) Diaphragm pump
US5242281A (en) Wobble plate pump
US20200011312A1 (en) Cylinder assemble structure for compact air compressor
KR102310254B1 (ko) 동력 분무기
JP2015021485A (ja) 手押しポンプ
JP3602576B2 (ja) 揺動型圧縮機
JPH09144666A (ja) 揺動型圧縮機
KR102478979B1 (ko) 워블 다이어프램 펌프
CN204729249U (zh) 微型真空泵
US20250180003A1 (en) Pump diaphragm with improved seal geometry
KR20010066579A (ko) 밀폐형 압축기의 피스톤핀 설치구조
KR0129267Y1 (ko) 편심캠을 이용한 오일 펌프